System for controlling at least two variable-geometry equipments of a gas turbine engine, particularly by rack

ABSTRACT

A system for controlling at least two variable-geometry equipments of a gas turbine engine is disclosed. The engine includes at least a first core rotating at a first speed and a second core rotating at a second speed. The first equipment includes at least one variable-pitch stator blade of a compressor of the first core and the second equipment includes at least one air bleed valve of a compressor of the second engine core moving between an open position at idle speed and a closed position at high speed. The system includes an actuator which actuates both equipments.

BACKGROUND OF THE INVENTION

The present invention relates to the general field of the control of variable-geometry equipments of a gas turbine engine. The invention more particularly relates to the optimization of the control of several equipments forming part of distinct cores of the engine.

“Variable-geometry equipment” means in this instance an equipment that is connected to a control member and of which the dimension, the shape, the position and/or the speed is or are capable of being modified, according to detected events or defined parameters, in order to act on the operation of the engine. Examples of variable-geometry equipments are air bleed valves (with variable aperture) of a low-pressure compressor, fixed blades of a variable-pitch high-pressure compressor, turbine blades of which the clearance at the tip is variable, variable flow-rate fuel pumps, etc.

“Core” conventionally designates a subassembly of a gas turbine engine comprising as main members a compressor and a turbine assembled on a single shaft. Typically, an engine may comprise a high-pressure core and a low-pressure core. The blades of the compressor and of the turbine of each core are rotated about the axis of the shaft onto which they are mounted.

DESCRIPTION OF THE PRIOR ART

Usually, the various cores of a gas turbine engine are designed to be able to operate independently of one another. Their rotation speeds are independent, even though they can be connected or correlated in certain operating regimes.

Also usually, because of this independence between the various cores of a gas turbine engine, in order to control variable-geometry equipments forming part of different cores, distinct control systems are provided for these distinct equipments. For this reason, controlling two variable-geometry equipments of two distinct cores requires two control circuits, two actuators, two power sources, etc. The result of this is that the weight, the cost and the space requirement of these control systems for the equipments are relatively high. Such a configuration is the one adopted in the European patent application of the applicant published under number EP 1 724 474.

For example, the low-pressure core of a dual-core turbojet may comprise one or more air bleed valves (often designated VBV which is the acronym for “Variable Bleed Valve”), while the high-pressure core may comprise one or more variable pitch stator blade stages (often called VSV, which is the acronym for “Variable Stator Vanes”). In order to reduce the weight of these equipments and their control members, it can be envisaged to install no VBV. Although the saving thus made is significant (the actuators, the servovalves, the pipework, the harnesses, etc. that are associated thereby are removed), the risks induced are considerable, particularly at idle speed if water or hail enters the engine causing an increased risk of stopping the latter.

Patent application FR 2 445 439 by the General Electric Company describes a single means for controlling air bleed valves of a low-pressure stage and of the variable pitch stator stages of a high-pressure stage, but this means controls both equipments in an essentially sequential manner, only the stator blades being actuated during normal operation of the turbomachine (that is to say above the idle speed).

SUMMARY OF THE INVENTION

The object of the invention is to propose a gas turbine engine with variable-geometry equipments belonging to the different cores of the engine and control of these equipments that is optimized.

Thus, the invention relates to a system for controlling at least two variable-geometry equipments of a gas turbine engine, the engine comprising at least a first core rotating at a first speed and a second core rotating at a second speed, the first equipment being a variable-pitch stator blade stage of a compressor of the first core traveling between a closed position at idle speed and an open position at high speed, the second equipment being at least one bleed valve of a compressor of the second core traveling between an open position at idle speed and a closed position at high speed, said system comprising an actuator which actuates both equipments.

By using a single actuator for controlling several (at least two) variable-geometry equipments, the control system makes it possible to reduce the number of parts of the gas turbine engine and thereby achieve the objective of the invention, while retaining said equipments on distinct cores, allowing them thereby to fulfill their function. The weight, the volume and the cost of a second control system are, at least largely, avoided, since the equipments of the first and second cores are actuated by the same actuator.

According to one embodiment, the control system is capable of controlling more than two variable-geometry equipments with the aid of a single actuator.

According to one embodiment, the actuator is controlled by the rotation speed of one of the engine cores. Therefore, the equipment of the other core is controlled by the rotation speed of said core, through the actuator.

In particular, since the engine comprises a low-pressure compressor and a high-pressure compressor, the variable-geometry equipment of the low-pressure compressor is controlled by the rotation speed of the high-pressure compressor. The laws of control of the actuators are therefore simplified.

According to one embodiment, in the case of an engine with a high-pressure core and a low-pressure core, the variable-geometry equipments of the high-pressure core are situated close to the low-pressure core (for example close to the upstream side of the high-pressure core). The mechanical connection between the actuator and the equipments that it controls is therefore made easier.

According to one embodiment, the first variable-geometry equipment comprises at least one variable-pitch stator blade of at least one stator-blade disk, belonging to the high-pressure compressor of a dual-core engine, that is to say an engine with a high-pressure core and a low-pressure core.

According to a particular embodiment in this case, since the engine comprises at least one blade disk comprising a plurality of variable-pitch stator blades, each mounted so as to pivot on a casing of the engine, a control ring surrounding the casing is connected to said blades, for example via levers, the actuator being capable of rotating the control ring, for example by means of an angle transmission member mounted on the casing.

According to one embodiment, the second variable-geometry equipment comprises at least one air bleed valve of the engine. This equipment may comprise one air bleed valve or a plurality of air bleed valves. They are, for example, one or more air bleed valves of the VBV type situated at the low-pressure compressor of a dual-core engine.

The control system of the invention may be adapted to control various types of equipment. In addition to those explained above, the variable-geometry equipments may notably comprise or form an element of one or more of the following devices:

-   -   an air bleed valve of the high-pressure compressor with         proportional aperture (often called “Transient Bleed Valve”         (TBV) or “Start Bleed Valve” (SBV));     -   an on/off high-pressure compressor air bleed valve (often called         “Handling Bleed Valve” (HBV));     -   an air flow regulation valve contributing to the control of         clearance in a low-pressure turbine (often called “Low Pressure         Turbine Active Clearance Control” (LPTACC)), or in a         high-pressure turbine (often called “High Pressure Turbine         Active Clearance Control” (HPTACC)).

According to one embodiment, the actuator of the control system comprises at least one movable actuation member the movements of which make it possible to actuate the variable-geometry equipments.

Preferably, the actuator is arranged to actuate the equipments thanks to the variations of a parameter of movement or of position of its movable actuation member. It is therefore possible to define, for each equipment, a law of actuation according to said movement or position parameter (mention will also be made of actuation parameter). The same actuation parameter makes it possible to control a plurality of (at least two) variable-geometry equipments.

More particularly, the actuator is arranged to actuate the first variable-geometry equipment by varying the actuation parameter in a range of actuation of the first equipment and to actuate the second variable-geometry equipment by varying the parameter of actuation in a range of actuation of the second equipment.

According to one embodiment, a means of disengagement is provided between the actuator and at least one of the equipments, said means being arranged to disengage said equipment from the actuator outside the range of actuation of said equipment; therefore, in such a range of the actuation parameter, irrespective of the variations of the parameter, the actuator does not (or not significantly) act on the equipment in question, which is therefore disengaged from the actuator. It is also said that such a range of values of the actuation parameter, in which the actuation member of the actuator is in movement but does not actuate the equipment in question, forms, for said equipment, a “free travel” of the actuation member. The disengagement device makes it possible to reserve a range of values of the actuation parameter solely for controlling the other equipment(s). This is advantageous when the equipment in question must not be affected even when the control of one of the other equipments that are controlled must be able to vary.

According to a particular embodiment, at least one portion of the range of actuation of the first equipment is outside the range of actuation of the second equipment. Control by a single actuator of two variable-geometry equipments may be made easier by the fact that the ranges of actuation of both equipments do not match totally, making it possible, outside the common zone, to actuate one equipment without actuating the other.

According to one embodiment, the ranges of actuation of the first and second equipments comprise a common zone. Therefore, both equipments may be actuated simultaneously in this common zone.

According to another particular embodiment, the ranges of actuation of the first and second equipments are not connected, that is to say that the ranges of actuation of the equipments have no common zone. Therefore, the equipments may be actuated in a sequential manner. Specifically, when the parameter of the actuator in the range of actuation of the first equipment is varied, these variations do not substantially induce any movement on the second equipment, and vice versa.

According to a particular embodiment, the range of actuation of one of the first and second equipments is entirely contained in the range of actuation of the other equipment. In this case, the equipments are actuated simultaneously in their common zone, which may have advantages depending on the nature of the equipment, as seen above; in addition, such an embodiment may make it possible to provide a greater amplitude of actuation for one of the two equipments.

According to one embodiment, the control system comprises return means keeping at least one equipment in a predetermined position, at least when the actuation parameter varies in a range situated outside the range of actuation of said equipment.

In such a range, this involves ensuring the correct position of the equipment in question.

Such return means may act on a part that is mechanically connected to the equipment in question so as to force the equipment into the predetermined position in the range situated outside its range of actuation; in the range of actuation of the equipment, the actuator opposes the action of these return means in order to force the equipment into another position.

According to a preferred embodiment of the invention, the actuator comprises a double-rack mechanism, each rack being arranged to actuate a variable-geometry equipment.

According to a particular embodiment, the actuator comprises a gearwheel arranged to drive the racks. The gearwheel, in particular, forms the actuation member described above; the actuation parameter of such an actuation member is the angular position of the gearwheel.

According to one embodiment, at least one of the racks comprises an oblong hole arranged to interact with a lug of a part that is mechanically connected to the equipment actuated by the rack, in order to form a means for disengaging said equipment outside its range of actuation.

The invention also relates to a gas turbine engine, comprising at least a first core rotating at a first speed and a second core rotating at a second speed, variable-geometry equipments forming part of distinct cores and the control system described above.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be better understood with the aid of the following description of the preferred embodiment of the gas turbine engine and of the system of the invention, with reference to the appended drawings, in which:

FIG. 1 represents an overview in section of the compressor of a gas turbine engine according to the invention;

FIG. 2 represents a view in perspective of a portion of the control system according to the invention for the actuation of the VSV blades and of the VBV valves of the engine of FIG. 1;

FIG. 3 represents a schematic top view of the actuator of the control system of FIG. 2, in a first actuation position;

FIG. 4 represents a schematic top view of the actuator of the control system of FIG. 2, in a second actuation position;

FIG. 5 represents a schematic top view of the actuator of the control system of FIG. 2, in a third actuation position;

FIG. 6 represents an alternative embodiment of a portion of the control system of FIG. 2; and

FIGS. 7 and 8 represent the possible laws of aperture of the VSV blades and of the VBV valves of the engine of FIG. 1 according to the rotation speed of its high-pressure core.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In a known manner, a gas turbine engine M, in this instance a dual-core turbojet with an axis X-X comprises, from upstream to downstream, a fan, not shown, a low-pressure compressor 2 (frequently called a “booster” by those skilled in the art), a high-pressure compressor 3, a combustion chamber, a high-pressure turbine, a low-pressure turbine and a nozzle for exhausting the gases (not shown). Hereinafter, the following abbreviations will be used: LP for low pressure and HP for high pressure.

The HP compressor 3 and the HP turbine are attached to a single shaft, called the high-pressure shaft, and therefore belong to the HP core of the engine M, while the LP compressor 2 and the LP turbine are attached to a single shaft, called the low-pressure shaft, and therefore belong to the LP core of the engine.

The HP compressor 3 comprises at least one stage 10 formed of a disk 10 a of movable blades and a disk 10 b of fixed blades (also called stator blades). Each disk 10 a, 10 b is formed of a plurality of blades placed radially about the axis X-X of the engine M. In this instance, the HP compressor 3 comprises a plurality of stages 10, with an alternation of fixed blade disks 10 b and movable blade disks 10 a. The blades are enveloped by a casing 12 which is centered on the axis X-X of the engine M in the conventional manner.

Of the fixed blade disks 10 b, at least the disk 10 b of a stage 10 comprises at least one blade 14 called a variable-pitch blade; in this instance, the disk 10 b comprises a plurality of such blades 14 and more precisely in this instance the totality of its blades 14 have variable pitch. In this instance, they are “VSV” (for “Variable Stator Vanes”) blades 14, already explained above. Each VSV blade 14 is mounted so as to pivot about an axis 16 (or pivot 16) which traverses the casing 12. The angular position of each VSV blade 14 may be adjusted by rotating its pivot 16.

The disk 10 b comprising VSV blades 14 belongs to a first variable-geometry equipment, belonging to the HP core. In this instance, the first variable-geometry equipment comprises a plurality of disks 10 b of VSV blades 14. The variable parameter of this equipment 10 b is the angle of the VSV blades 14 about their pivot 16; in this instance, all the VSV blades 14 of a disk 10 b are simultaneously rotated by a ring 22 for controlling (or actuating) the disk 10 b of VSV blades 14.

The control ring 22 is of generally circular shape; it surrounds the casing 12 and is centered on the axis X-X of the engine M. The synchronized modification of the angular position of the VSV blades 14 is therefore obtained by rotating the control ring 22 about the axis X-X of the engine, in a known manner.

The engine M comprises a second variable-geometry equipment 110 comprising in this instance at least one air bleed valve 110, in this case a plurality of bleed valves 110. In this particular case they are “VBV” (for “Variable Bleed Valves”) valves, already explained above. The variable parameter of such a variable-geometry equipment 110 is the angle of aperture of the VBV valves 110. The VBV valves 110 belong to the LP core 2 of the engine M, that is to say that they are situated at the low-pressure compressor. The function of the VBV valves 110 is to bleed air to the outlet of the LP compressor 2 in order to reduce the risks of malfunction of this compressor 2 when it operates in particular conditions.

The control system is arranged to actuate the VSV blades 14 (first equipment 10 b) and the VBV valves 110 (second equipment 110). Accordingly, the control system comprises an actuator 24, in this instance a double-rack actuation mechanism 24, which is mechanically connected to the first equipment 10 b and to the second equipment 110 in order to actuate them, that is to say in this instance in order to control their position by moving them.

The actuator 24 comprises a first link rod 24A, for controlling the position of the VSV blades 14, connected to a mechanism for transmitting movement to the disks 10 b of VSV blades 14, and a second link rod 24B, for controlling the position of the VBV valves 110, connected to a mechanism for transmitting movement to the VBV valves 110. The control link rods 24A, 24B fulfill a function of transmitting movement from the actuator 24 to the variable-geometry equipments 10 b, 110. With reference to FIG. 3, the actuator 24 comprises a housing 25 in which is mounted a gearwheel 50 (or pinion 50) for driving the control link rods 24A, 24B; the gearwheel 50 is the member 50 for actuating the actuator 24; the movement parameter of this actuation member 50, making it possible to control the geometry of the equipments 10 b, 110 by actuating them, is the angular position of the gearwheel 50. The gearwheel 50 is mounted so as to rotate about a shaft 51 and comprises, at its periphery, a plurality of teeth 52. These teeth 52 are arranged to mesh with teeth 53A, 53B arranged on a wall of each control link rod 24A, 24B. The two link rods 24A, 24B are mounted parallel with one another in a diametrically opposed manner relative to the gearwheel 50. Each control link rod 24A, 24B with its teeth 53A, 53B forms a rack 24A, 24B driven in translation relative to the housing 25 by the gearwheel 50. As indicated in FIG. 3, a rotation of the drive gearwheel 50 in the counterclockwise direction causes the racks 24A, 24B to be moved out of the housing 25. The gearwheel 50 is rotated by appropriate driving means, for example an electric motor or a hydraulic motor.

The housing 25 comprises two posts 25A, 25B for guiding each rack 24A, 24B in rectilinear translation relative to the housing 25. Each rack 24A, 24B is therefore forced to move in translation relative to the housing 25 since it is contained laterally between a wall of the housing 25 and a guide post 25A, 25B respectively.

In order to confer on the various parts of the movement transmission mechanism, from the racks 24A, 24B up to the variable-geometry equipments 10 b, 110, the degrees of freedom that are sufficient for their movements, the housing 25 of the actuator 24 is in this instance mounted so as to pivot on the casing 12 of the engine M, in this particular case about a shaft collinear with the shaft 51 of the gearwheel 50 of the actuator 24. The housing 25 can therefore pivot in order to accompany the translation of the racks 24A, 24B, which are constrained by the movements of the parts to which they are connected, described below.

Therefore, a single actuator 24 can control two variable-geometry equipments 10 b, 110 of two distinct cores of a gas turbine engine, each rack 24A, 24B of the actuator 24 being operated by the gearwheel 50 in order to actuate an equipment 10 b, 110 via a movement-transmission mechanism.

Note here that the control system comprises means, not shown, for returning the VBV valves 110 to the closed position; these return means keep the VBV valves 110 in the closed position by default, in particular when the actuation parameter varies in a range situated outside the range of actuation of the VBV valves 110. The operation of these means will be explained in detail below.

In the following description, elements that are different but have similar or equivalent shapes and/or functions will be designated by identical reference numbers.

The drive mechanism between the actuator 24 and the VSV blades 14 will be described first of all.

Each pivot 16 of the VSV blades 14 is connected to one end of a link rod 18 or control lever 18 the other end of which is articulated about a trunnion 19 attached to the control ring 22 of the disk 10 b in question.

The ring 22 comprises at least one yoke 27 to which is attached one end of a control link rod 32, of the stretching screw type, which extends substantially tangentially to the ring 22. The other end of the control link rod 32 is secured to an angle transmission member 26, 26′ mounted so as to pivot on a housing 28 of the casing 12 of the engine M. The angle transmission member 26, 26′ is connected to the actuator 24 and therefore transmits the movements from the actuator 24 to the control ring 22.

There are two types of angle transmission members 26: a “leader” angle transmission member 26, which is the angle transmission member 26 directly connected to the actuator 24 and the “follower” angle transmission members 26′, which are directly or indirectly connected to the leader angle transmission member 26. In FIG. 2, the leader angle transmission member 26 and a follower angle transmission member 26′ are shown; the leader angle transmission member 26 is more precisely T-shaped while the follower angle transmission member 26′ is L-shaped.

The control link rod 32 is attached to the end of a first branch 34 of the T, the end of the rack 24A of the actuator 24 being attached, in an articulated manner, to the end of the second branch 42 of the T which is in the extension of its first branch 34.

The third branch 38 of the T, perpendicular to the other two, is connected at its end to a bar 30 called the synchronization bar, itself connected to one end of a branch 40 of the follower angle transmission member 26′, in a known manner, in order to transmit the movements from the leader angle transmission member 26 to the follower angle transmission member 26′. The other branch 36 of the follower angle transmission member 26′ is connected to one end of a control link rod 32 connected to a yoke 27 of the second control ring 22 shown in FIG. 2, to which the transmission of movement takes place in a quite similar manner to the transmission of movement from the leader angle transmission member 26 to the first control ring 22.

The actuator 24 can rotate the control rings 22 of the disks 10 b of VSV blades 14 via the leader angle transmission member 26 which transmits the movement from the first rack 24A of the actuator 24 to the rings 22. The transmission of movement from a leader angle transmission member 26 to a first ring 22 for controlling VSV blades 14 and to the follower angle transmission members 26′ and other rings 22 for controlling VSV blades 14 is known per se by those skilled in the art and does not require more detailed development in the context of the present description.

The mechanism for transmitting movement between the second rack 24B of the actuator 24 and the VBV valves 110 will not be described in detail. The second rack 24B of the actuator is connected to the VBV valves 110 via a kinematic chain which can easily be defined by those skilled in the art depending upon the various parameters in their possession: the number of VBV valves 110 to be controlled, the distance from the actuator 24 to the VBV valves 110, whether or not a gearing-down of the movement is necessary, etc.

In this instance, and with reference to FIGS. 3 to 5, the second rack 24B of the actuator, for controlling the VBV valves 110, is connected, via its end protruding out of the housing 25, to the end of a link rod 54 for transmitting movement to the VBV valves 110. The end of the rack 24B is, for this purpose, pierced with an oblong hole 55, while the link rod 54 for transmitting movement comprises, at its end connected to the rack 24B, a lug 56 arranged to be able to slide in the oblong hole 55.

At the end of the rack 24B, the oblong hole 55 interacts with the lug 56 of the transmission link rod 54 in order to form a sliding connection, the function of which is to create a free travel in the kinematic link between the rack 24B of the actuator 24 and the VBV valves 110. In other words, this sliding link forms a means of disengagement between the actuator 24 and the VBV valves 110 outside of the range of actuation of the VBV valves 110. When the rack 24B is operated so that its oblong hole 55 slides on the lug 56, it does not operate the link rod 54 for transmitting movement and therefore does not act on the VBV valves 110; the actuator 24 is activated (the gearwheel 50 is made to move) but its action transmits no movement to the VBV valves 110, although it can transmit movements to the disks 10 b of the VSV blades 14. It is only when the oblong hole 55 abuts on the lug 56, in this instance via its right end wall in FIG. 3, that a movement of the rack 24B causes a movement of the link rod 54 for transmitting movement and therefore of the VBV valves 110.

Moreover, as indicated above, the system comprises means, not shown, for returning the VBV valves 110 to the closed position. Such return means may, for example, comprise a mechanism with a spring for returning the VBV valves 110 to the closed position, the structure of which is accessible to those skilled in the art and requires no detailed description; such a mechanism acts directly or indirectly on the link rod 54 for transmitting movement to the VBV valves 110, in order to return the latter to the closed position; the return force that they exert on the VBV valves 110 is less than the force that the actuator 14 can transmit when it actuates the VBV valves 110. Therefore, when the right wall of the oblong hole 55 abuts on the lug 56 of the link rod 54 for transmitting movement, the actuator 24 transmits to the link rod 54—and therefore to the VBV valves 110—forces greater than the return force that is exerted by the return means and that therefore opposes their action, making it possible to open the VBV valves 110. Conversely, if the actuator 24 does not force the link rod 54 for transmitting movement in the direction of opening of the VBV valve 110, the return means push back the link rod 54 for transmitting movement to the closed position of the VBV valves 110 (up to the position determined by the position of the link rod 54 for transmitting movement); this is particularly the case in a movement of the second rack 24B from left to right in the representations of FIGS. 3 to 5.

The operation of the control system will now be described with reference to FIGS. 3 to 5 and 7.

FIG. 7 shows the relative opening laws of the VSV blades 14 and of the VBV valves 110 as a function of the speed N of rotation of the HP core. The higher the value of a curve, the more open is the corresponding variable-geometry equipment 10 b, 110. The open position of the VSV blades 14 corresponds to the position in which they allow the largest air flow to pass into the HP compressor 3; the open position of the VBV valves 110 corresponds to the position in which they take the maximum air flow rate from the LP compressor 2 (in order to move the operating line of the compressor away from the surge line).

In a first phase P1, at low speed, the VBV valves 110 are open while the VSV blades 14 are closed. In a second phase P2, at intermediate speed, the VBV valves 110 are progressively closed as the speed N of the HP core increases while the VSV blades 14 are progressively opened as the speed N of the HP core increases; at the end of the second phase P2, the VBV valves 110 are almost completely closed while the VSV blades 14 are approximately two-thirds open. In a third phase P3, the closing of the VBV valves 110 is completed while the opening of the VSV blades 14 is progressively completed, as the speed N of the HP core increases.

Therefore, the two variable-geometry equipments 10 b, 110 are operated by the speed of the HP core. In particular, the VBV valves 110, belonging to the LP core, are controlled by the rotation speed N of the HP core. The result of this is a simplification of the definition of the laws of opening and guaranteed good synchronization between the openings and closures of the variable-geometry equipments 10 b, 110, since these openings and closures depend on the same single parameter: the rotation speed N of the HP core.

It can be seen that, during the third and second phases P3, P2, if the curves are followed in the direction of the decreasing speeds N, the VSV blades 14 begin to close before the VBV valves 110 begin to open. Such a difference in the actuation of the equipments 10 b, 110 is possible thanks to the disengagement (on the free travel) of the oblong hole 55 on the lug 56.

The law of actuation of the VSV blades 14 and of the VBV valves 110 as a function of the actuation parameter (the angular position of the gearwheel 50), making it possible to obtain the closure of the VSV blades 14 and the opening of the VBV valves 110, will be more specifically described with reference to FIGS. 3 to 5.

In the configuration of FIG. 3, the racks 24A, 24B are in a position retracted into the housing 25. In this configuration, the branch 42 of the leader angle transmission member 26 connected to the first rack 24A extends perpendicularly to the latter: the VSV blades 14 are in the open position. Moreover, the link rod 54 for transmitting movement to the VBV valves 110 extends perpendicularly to the second rack 24B: the VBV valves 110 are in the closed position.

In the configuration of FIG. 4, the gearwheel 50 has been rotated in the counterclockwise direction and the racks 24A, 24B have therefore been driven toward the outside of the housing 25. The first rack 24A has caused in its movement a rotation of the leader angle transmission member 26 and therefore the beginning of the closure of the VSV blades 14. During this time, the second rack 24B has traveled a distance corresponding to the dimension of the length of the oblong hole 55 (a dimension parallel to the direction of translation of the second rack 24B); this movement therefore has moved the transmission link rod 54 not at all (or not much) and has therefore not moved the VBV valves 110. Therefore, the oblong hole 55 has allowed a free travel of the rack 24B for controlling the VBV valves 110 while the rack 24A for controlling the VSV blades 14 moved the latter. Because of the pivot-mounting of the housing 25, a slight movement of the transmission link rod 54 may occur.

In the configuration of FIG. 5, the gearwheel 50 has also been rotated in the counterclockwise direction and the racks 24A, 24B are in their position farthest out of the housing 25. In this configuration, the rack 24A for controlling the VSV blades 14 has rotated the leader angle transmission member 26, this member 26 being in its most inclined position relative to the first rack 24A; the VSV blades 14 are therefore in the closed position. Between the configuration of FIG. 4 and the configuration of FIG. 5, the rack 24B for controlling the VBV valves 110 has moved in translation relative to the housing 25, moving in its travel the end of the transmission link rod 54 since, in the configuration of FIG. 4, the oblong hole 55 is in abutment, via its right end, on the lug 56; the operation of the transmission link rod 54 causes the VBV valves 110 to open.

Note that, in FIGS. 3 to 5, the pivoting of the housing 25 has not been shown in order to simplify the description.

The closure of the VBV valves 110 and the opening of the VSV blades 14 is simply obtained by driving the gearwheel 50 in the clockwise direction, from the configuration of FIG. 5 to that of FIG. 3, while passing through the configuration of FIG. 4. During such a rotation of the gearwheel 50:

-   -   the VSV blades 14 are driven directly from their closed position         to their open position by a rotation of the ring 22, which is         driven by the rotation of the leader angle transmission member         26 itself directly driven by the link rod 24A for controlling         the VSV blades 14;     -   the VBV valves 110 are driven from their open position to their         closed position by the return means acting (directly or         indirectly) on the link rod 54 for transmitting movement;         specifically, the rotation in the clockwise direction of the         gearwheel 50 causes a movement in translation, into the housing         25 of the actuator 24, of the second control link rod 24B; the         link rod 54 for transmitting movement follows this movement         because it is forced by the return means into this movement (but         simultaneously immobilized and therefore guided by the wall of         the oblong hole 55 of the second rack 24B, the position of which         is defined by the angular position of the gearwheel 50).

As defined above, the range of actuation, for each variable-geometry equipment 10 b, 110, corresponds to the range of values of the parameter of the actuation member 50 of the actuator 24, in other words to the angular position of the gearwheel 50 about its shaft 51, for which a movement of the actuation member 50 causes an actuation of the equipment in question 10 b, 110. In the embodiment shown in FIGS. 3 to 5, the ranges of actuation of the two equipments 10B, 110 intersect, that is to say that they have a common zone; therefore, the opening of the VBV valves 110 begins before the VSV blades 14 finish closing. The precise moment at which the opening of the VBV valves 110 begins during the closure of the VSV blades 14 is defined by the length L of the oblong hole 55. An increase in the length of this hole 55 delays the beginning of opening of the VBV valves 110, while shortening it advances the opening.

Therefore, it is possible to control the opening of the variable-geometry equipments 10 b, 110 depending upon the speed N of the HP core. Accordingly, the actuator 24 is controlled by an electronic control unit (not shown). The information on the speed N of the HP core is entered into the control unit which uses this information to control the rotation of the gearwheel 50 and therefore, as explained above, to actuate the variable-geometry equipments 10 b, 110 and therefore control their geometry. The actuator 24 is configured according to the manner in which it is desired to be able to slave the geometry of the equipments 10 b, 110 to the speed N of the HP core.

According to an alternative embodiment, the ranges of actuation of the variable-geometry equipments 10 b, 110 are unconnected, that is to say that the geometries of the equipments 10 b, 110 may be controlled in a sequential manner. It is therefore possible to apply relative opening laws of the VSV blades 14 and of the VBV valves 110 like those shown in FIG. 8, which will now be described.

In a first phase P′1, corresponding to the lowest speeds N, the geometry of the equipments 10 b, 110 remains constant. The VSV blades 14 are then in the closed position while the VBV valves 110 are in the open position.

In a second phase P′2, the VBV valves 110 are progressively closed while the VSV blades 14 remain in the open position.

In a third phase P′3, the geometry of the equipment 10 b, 110 remains substantially unchanged.

In a fourth phase P′4, the VSV blades 14 are progressively opened while the VBV valves 110 remain closed.

For the application of such actuation laws, it is necessary to be able to actuate the equipments 10 b, 110 in a sequential manner.

To this end, and according to a particular embodiment, the control system may be modified in order to provide a means of disengagement between the first rack 24A of the actuator 24 and the VSV blades 14 once the VSB blades 14 are closed, the oblong hole 55 of the second rack 24B of the actuator 24 having dimensions such that, throughout the closure phase of the VSV blades 14, the VBV valves 110 are disengaged, their opening beginning only after the total closure of the VSV blades 14, while the latter are disengaged from the actuator 24 during the opening of the VBV valves 110.

FIG. 6 shows a possible embodiment for producing such a control system. In the latter, the oblong hole 55, not shown, of the second rack 24B of the actuator 24 has sufficiently large dimensions for the free travel of the second rack 24B to take place throughout the whole range of actuation of the VSV blades 14, that is to say throughout the movement of the gearwheel 50 corresponding to the closure of the VSV blades 14. In addition, the first rack 24A is modified to comprise an oblong hole 55′ at its end, the branch 42 of the leader angle transmission member 26 connected to the first rack 24A comprising, at its end connected to the rack 24A, a lug 56′ arranged to be able to slide in the oblong hole 55′; moreover, means for returning the leader angle transmission member 26 to the closed position of the VSV blades 14 are provided; the other elements of the control system are identical to those of the control system of FIGS. 3 to 5.

In this way, during the rotation of the gearwheel 50 in the counterclockwise direction (from a position corresponding to that of FIG. 3 to a position corresponding to that of FIG. 5), the oblong hole 55′ is first of all moved to the right and the lug 56′ of the branch 42 of the leader angle transmission member 26 follows this movement, driven in this movement by the means for returning the VSV blades 14 to the closed position. During this rotation of the gearwheel 50, the second rack 24B is driven in translation to the left and its oblong hole 55 slides on the lug 56 of the link rod 54 for transmitting movement which remains in position, retained by the means for returning the VBV valves 110 to the closed position. Therefore the VSV blades 14 are made to close while the VBV valves 110 remain fixed in the closed position.

Once the VSV blades 14 are in the closed position, if the rotation of the gearwheel 50 is continued, the first rack 24A continues its rightward travel, the oblong hole 55′ sliding on the lug 56′ of the branch 42 of the leader angle transmission member 26 which remains in position, held by the means for returning the VSV blades 14 to the closed position. During this time, the second rack 24B continues its leftward movement, the right wall of its oblong hole 55 in abutment on the lug 56 of the link rod 54 for transmitting movement moving the latter: the second rack 24B therefore operates the VBV valves 110 to their open position. Therefore, the VBV valves 110 are made to open while the VSV blades 14 remain fixed in the closed position.

Moreover, during the rotation of the gearwheel 50 in the clockwise direction (from a position corresponding to that of FIG. 5 to a position corresponding to that of FIG. 3), the first rack 24A is moved to the left, its oblong hole 55′ sliding first of all on the lug 56′ of the branch 42 of the leader angle transmission member 26, held in position by the means for returning the VSV blades 14 to the closed position. During this time, the second rack 24B is moved to the right and the means for returning the VBV valves 110 to the closed position move the latter from their open position to their closed position, since the lug 56 of the control link rod 54 follows the translation of the right wall of the oblong hole 55. Therefore the VBV valves 110 are made to close while the VSV blades 14 remain fixed in the closed position.

When the clockwise rotation of the gearwheel 50 is continued, the right wall of the oblong hole 55′ of the first rack 24A butts against the lug 56′ of the branch 42 of the leader angle transmission member 26 and rotates the latter against the action of the means for returning the VSV blades 14 to the closed position: the VSV blades 14 are therefore moved from their closed position to their open position. During this time, the VBV valves 110 remain in the closed position, held in this position by the means for returning the VBV valves 110 to the closed position, while the oblong hole 55 of the second rack 24B slides on the lug 56 of the link rod 54 for transmitting movement. Therefore the VSV blades 14 are made to open while the VBV valves 110 remain fixed in the closed position.

The VSV blades 14 and the VBV valves 110 are therefore clearly operated in a sequential manner. 

1. A system for controlling at least two variable-geometry equipments of a gas turbine engine, the engine comprising at least a first core rotating at a first speed and a second core rotating at a second speed, the first equipment comprising at least one variable-pitch stator blade of a compressor of the first core moving between a closed position at idle speed and an open position at high speed, the second equipment comprising at least one compressor air bleed valve of the second engine core traveling between an open position at idle speed and a closed position at high speed, said system comprising: an actuator which actuates both equipments, wherein the actuator comprises at least one movable actuation member which actuates the variable-geometry equipments, and wherein the actuator comprises a double-rack mechanism, each rack being arranged to actuate at least one of the variable-geometry equipments.
 2. The control system as claimed in claim 1, wherein the actuator is controlled by the rotation speed of one of the engine cores.
 3. The control system as claimed in claim 2, wherein the engine comprises a low-pressure core and a high-pressure core, the actuator being controlled by the rotation speed of the high-pressure core.
 4. The control system as claimed in claim 1, wherein the first variable-geometry equipment comprises at least one variable-pitch stator blade of a high-pressure compressor of a dual-core engine.
 5. The control system as claimed in claim 1, wherein the second variable-geometry equipment comprises at least one air bleed valve of the engine, situated in a low-pressure compressor of a dual-core engine.
 6. The control system as claimed in claim 1, wherein, with the actuator being arranged to control the equipments based on variations of a parameter of actuation of its movable actuation member, the actuator is arranged to actuate the first equipment by varying the actuation parameter in a range of actuation of the first equipment and the second equipment by varying the actuation parameter in an actuation range of the second equipment.
 7. The control system as claimed in claim 1, wherein a means of disengagement is provided between the actuator and at least one of the equipments, said means being arranged to disengage said equipment from the actuator outside the range of actuation of said equipment.
 8. The control system as claimed in claim 1, wherein the actuator comprises a gear wheel arranged to drive the racks.
 9. The control system as claimed in claim 1, wherein at least one of the racks comprises an oblong hole arranged to interact with a lug of a part that is mechanically connected to the equipment actuated by the rack, in order to form a means for disengaging said equipment outside its range of actuation.
 10. A gas turbine engine, comprising at least a first core rotating at a first speed and a second core rotating at a second speed, variable-geometry equipments forming part of distinct cores and the control system of one of claim 1-5, 6-7, or 8-9. 